• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
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  • 优先权
    • 专利摘要:
    nut. in order to optimize a nut and a method for manufacturing a nut, comprising a nut body provided or can be provided with an internal thread, which has a polygonal section with a polygonal outer contour which, on the one hand, presents corner areas and, on the other hand, it has key surfaces that lie between the corner areas, which extend into planes of key surfaces that pass according to patterns, such that this nut has more optimized mechanical properties possible with as little weight as possible it is suggested that the nut body has several recesses starting from the respective key surface planes into the nut body, in the direction of the hole.
    公开号:BR112014018857B1
    申请号:R112014018857-2
    申请日:2013-02-01
    公开日:2021-08-24
    发明作者:Peter Unseld；Günther Meßmer
    申请人:Hewi G. Winker Gmbh & Co. Kg；
    IPC主号:
    专利说明:

    [001] The invention relates to a nut, comprising a nut body provided or which may be provided with an internal thread in the area of a hole, which has a polygonal section with an external polygonal contour which, on the one hand, features corner areas and, on the other hand, features key surfaces that lie between corner areas, which extend in patterned key surface planes.
    [002] Nuts of this type are polygonal nuts known from the prior art, whereby the position and alignment and course of the key surfaces result, for example, from normative foundations, for example, DIN EN 1661, 1663, 1664, 1667, DIN EN ISO 4032 - 4036, DIN EN ISO 8673 - 8675, DIN EN ISO 7040 - 7042, DIN EN ISO 7719, DIN EN ISO 10513 as well as DIN EN ISO 4759 - 1.
    [003] The nuts can already be provided with an internal thread, or just be provided with a hole, in which an internal thread is formed when tightening self-drilling or self-cutting screws.
    [004] In the case of nuts of this type there is a need to reduce their weight with the most advantageous mechanical properties of use possible.
    [005] Therefore, it is the task of the invention to optimize a nut according to the invention, of the type described at the beginning, in such a way that this nut presents the most optimized mechanical properties possible with the smallest possible weight.
    [006] In a nut according to the invention, of the type described at the beginning, this task is solved by the fact that the nut body has several recesses, starting from the respective key surface planes into the nut body, in the hole direction.
    [007] The advantage of the solution according to the invention should be seen in the fact that, through the recesses that extend into the nut body, material savings and, therefore, a reduction in weight can be obtained without negatively affect the mechanical properties of the nut body.
    [008] With respect to the arrangement of recesses, in this case, no more detailed indications were made.
    [009] Thus, an advantageous solution foresees that, starting respectively from the planes of keys surfaces that are opposite each other, the recesses extend into the nut body.
    [010] In the simplest case these would be two planes of keys surfaces that are opposite each other, starting from which the recesses extend into the nut body.
    [011] But they can also be multiple planes of keys surfaces, from which the recesses extend into the nut body.
    [012] However, even more advantageous is the saving of material if, starting from each plane of keys surfaces of the polygonal section, a recess extends into the body of the nut.
    [013] With respect to the extension of the recess into the nut body, in the context of the execution examples described so far, no more detailed indications have been made.
    [014] Thus, an advantageous solution provides that the recess extends from the respective plane of keys surfaces to a support coating of the thread that involves stabilizing the internal thread, i.e., that the recess only passes to the support coating of the thread, however not beyond this coating.
    [015] In this case, the thread support coating is an area of the nut body closed in the circumference direction, which involves stabilizing the internal thread, and takes care that, in the event of a request for a threaded pin screwed into this thread, or of a screw screwed into this thread, the internal thread does not deform, in particular, does not widen beyond a defined value and thereby lose its shape or form strength, necessary for the admission of force and/or moments .
    [016] In this case, it is particularly advantageous if, starting from an external diameter of the internal thread, the supporting coating of the thread has a minimum radial thickness, which amounts to at least 0.05 times the external diameter of the internal thread.
    [017] In this case, a radial minimum thickness is measured at the thinnest point in the radial direction of the thread supporting coating, which in particular is an integral part of the nut body, and at each point presents the minimum radial thickness, in such a way that, through the minimum radial thickness, the stability of the thread-supporting coating is fixed.
    [018] In this case, the minimum radial thickness of the thread support coating can be invariable in the direction of the central axis.
    [019] But it is also conceivable that the minimum radial thickness of the thread support coating is variable in the direction of the central axis.
    [020] In principle, in the solution according to the invention it is conceivable to execute the nut body in such a way that this body extends between a first front side and a second front side and, in this case, each of the front sides is suitable for the purpose of admitting a body or an element for fastening them by means of the nut.
    [021] In order to be able to optimize, however, the nut according to the invention, in terms of introducing force into the nut body, it is preferably provided that the nut body has a first front side, executed with a pressure surface as the pressure side, and a second front side away from the pressure side, between which the nut body extends.
    [022] This solution has the advantage that, with this, the nut can be optimized in such a way that, in the area of the pressure side, the forces that arise with the nut, during the admission of a body or an element, act on the nut body and are admitted by this body, while in the case of the second front side it must be assumed that this side does not suffer any direct force input.
    [023] In the case of such a nut, for example, it is provided that the recess extends to the second front side, since in the area of the second front side there should not be a force admission of the nut body, in such a way that the forces arising in the area of the second front side are the lowest.
    [024] In addition, it is possible to execute the nut body in such a way that the recess extends to the depression side, in which case, the resistance to the shape of the pressure side needs to be sufficiently large so that it absorbs the loads planned.
    [025] In another form of execution, it is provided that the recess extends only through a partial section of the extension of the nut body, from one front side to the other front side, in such a way that the recess does not reach the other front side.
    [026] Another advantageous solution provides that the recess extends to a pressure bottom provided on the pressure side and therefore ends at the pressure bottom, such that, in the pressure side area, the nut body experiences additional stability through the pressure bottom.
    [027] As an alternative or complement to this, however, it is provided that the recess extends to a pressure flange provided on the pressure side, which extends radially beyond the polygonal section.
    [028] Also with respect to the minimum thickness of the thread support coating, in the case of the existence of a pressure side of the nut body it is advantageous if, in the area of the pressure side, the minimum radial thickness of the thread support coating is , at least as large as the area on the second front side.
    [029] It is even more advantageous if the minimum radial thickness of the thread support coating in the area of the pressure side is greater than in the area of the second front side, since in the area of the second front side there are peripheral loads of the thread support coating through the interaction of forces between the pressure side and the thread than in the area of the second front side, such that in this way the nut body can be optimized in terms of the loads that They emerge.
    [030] It is particularly advantageous if the thread supporting coating has an increasing radial minimum thickness with increasing extension from the second front side to the pressure side, since, in this way, starting from the second front side, ideally Peripheral loads of the thread supporting coating can be taken into account by increasing through the interaction of forces between the pressure side and the thread.
    [031] In terms of the formation of the surfaces of keys, so far no more detailed indications have been made.
    [032] Thus, an advantageous solution provides that, in each plane of key surfaces, there are areas of key surfaces adjacent to the corner areas that are opposite each other, between which is the respective recess.
    [033] This means that, the respective recess divides at least two areas of key surfaces, which respectively extend after the corner areas, and through the recess are separated at least partially from each other, and together form the surface of keys.
    [034] In terms of the minimum expansion of the key surface areas in a transverse direction between the corner areas, the transverse direction passing parallel to an interval direction of the corner areas, it is preferably provided that, in each cross-sectional plane that passes perpendicularly to a central axis of the internal thread, through the polygonal section, the sum of the expansion of the key surface areas in a transverse direction between, respectively, two successive corner areas matters at least in 10%, even better at least 15%, in particular at least 20% of a range of these corner areas in the transverse direction.
    [035] This means that the key surface formed from the two key surface areas has been reduced to ten percent of the extent in the transverse direction, in relation to the expansion of the key surface in the case of non-existent recess.
    [036] In principle, it is conceivable to choose differently the expansion of the areas of respectively individual keys surfaces, given that the sum of the expansions represents 10% of the interval of the corner areas.
    [037] This would be conceivable, for example, if an ideal adaptation of the key surface areas to the loads of the nut body were to take place during tightening or loosening.
    [038] For example, in the case of a nut body, which primarily must be fixed and then, in general, is no longer loose, it is conceivable to choose the two areas of keys surfaces differently, for example, execute the area of heavily loaded wrench surfaces in the nut body bolt tightening wider than the area of less loaded wrench surfaces.
    [039] A simplified embodiment provides that the two areas of keys surfaces in the transverse direction present approximately the same expansion, preferably, the same expansion in the transverse direction.
    [040] In terms of the formation of the recesses themselves, so far no more detailed indications have been made.
    [041] With respect to their extension the recesses could have any shapes parallel and radial to the central axis, that is, they could have free-form surfaces.
    [042] In addition, each of the recesses of the nut body may differ in its shape and/or dilation from the other recesses.
    [043] For example, the recesses respectively arranged on opposite sides of the nut body are executed in a similar way.
    [044] In particular, nothing has been presented about the cross-sectional shape of the executions.
    [045] Thus, an advantageous solution provides that the recesses have the same cross-sectional shape, in a cross-sectional plane that passes respectively perpendicular to a central axis of the internal thread, through the polygonal section.
    [046] For example, it is conceivable that the shape of the cross-section of the recesses is similar to a U in the respective cross-sectional plane.
    [047] But it is also conceivable that the shape of the cross-section of the recesses in the respective cross-section plane is approximated to a cross-sectional shape similar to a circle segment, or to a rectangular or V-shaped cross-section shape.
    [048] An advantageous solution provides that the recesses have a cross-sectional shape, which is determined by a background area, and that connects to the sidewall areas adjacent to the background area, which pass transversely to the respective plane of keys surfaces.
    [049] In this case, for example, it is conceivable that the recesses are executed in such a way that they present a cross-sectional shape, which is determined by a concave domed bottom area, and that connects the sidewall areas.
    [050] Regarding the variation in the shape of the recess cross section, so far no more detailed indications have been made.
    [051] Thus, it is foreseen that the recess has a constant or variable cross-sectional shape with an extension in a direction parallel to the central axis.
    [052] In particular, for example, it is conceivable that a range of the bottom area of a central axis of the internal thread is, in essence, constant along the length of the recess in the direction of the central axis.
    [053] As an alternative to this, however, it is also conceivable that the background area with the extension presents a variable range from the central axis in the direction of the central axis.
    [054] For example, it is provided that the recess is provided with a bottom area that passes inclined in relation to the central axis, which passes, for example, to the respective plane of keys surfaces.
    [055] Alternatively or complement the characteristics described above of the solution according to the invention, the task mentioned at the beginning is also solved by a nut of the type described at the beginning according to the invention, due to the fact that the internal thread it is manufactured to form the nut as a safety nut, as an internal thread corresponding to a standard stroke, however, through plastic deformation of the nut body, it is performed deviating from the standard stroke.
    [056] The advantage of the solution according to the invention should be seen in the fact that, only through the plastic deformation of the nut body is there the possibility of manufacturing a lock nut, which, therefore, has ideal mechanical properties with as little weight as possible, as no additional elements are foreseen in the nut body, which are normally necessary to obtain the necessary tightening torque for a lock nut.
    [057] With this, the nut according to the invention has mechanical properties, likewise, improved or optimized with as little weight as possible.
    [058] The defined tightening torque required for the function according to the invention as a locknut can be obtained, in particular, by the fact that, due to the plastic deformation of the nut body, the internal thread has variable radial intervals of the central axis, which deviate from a standard course, and/or interval courses or threads, which deviate from a standard course, such that a screwing of a threaded pin or a screw deforms the body of the nut plastically deformed, in turn, in an elastoplastic way in the direction of the standard measure, so that the tightening torque arises.
    [059] In the simplest case, on this occasion it is foreseen that, due to the plastic deformation of the nut body, the internal thread is executed not round in relation to the central axis.
    [060] Another advantageous solution provides that the internal thread has deformed thread areas arranged at intervals of equal angles to the central axis, whose interval of the central axis is reduced in relation to a standard course, that is, its interval is smaller than in a run according to standards.
    [061] In the simplest case it is a pair of deformed thread areas, which are opposite each other, whose central axis interval is reduced.
    [062] In another advantageous embodiment, the defined tightening torque required for the locknut according to the invention can be appropriately obtained by the fact that the internal thread has several thread areas alternative or complementary deformed, arranged with symmetry of two digits or several digits in relation to the central axis, whose interval is reduced in relation to a standard course.
    [063] For example, several deformed thread areas are provided, which are opposite each other in pairs in relation to the central axis, whose interval is reduced in relation to a standard measurement, or, for example, three or several areas of deformed threads, evenly distributed on the circumference, whose interval is reduced in relation to a standard course.
    [064] A particularly suitable execution of the nut according to the invention provides that the body of the nut is plastically deformed through the action of force on corner areas that are opposite each other, in relation to the central axis.
    [065] As an alternative to this, another solution provides that the body of the nut is plastically deformed through the action of force on areas of the bottom and/or areas of the side wall of recesses, which are opposite each other, in relation to the central axis.
    [066] In this case, it is particularly advantageous if the force actuation occurs in an upper area of the polygonal section, since the nut body is plastically deformed, preferably in the upper area with forces smaller than in the area of a pressure side of it.
    [067] Another alternative solution provides that the body of the nut is plastically deformed through the action of force in the area of an outer corner of the second front side.
    [068] In particular, a solution provides that the internal thread has deformed thread areas, with a course deviating from a standard course, and, for example, its pitch course is varied in relation to a standard pitch, this means that, for example, a range of threads from each other is larger or smaller than in an illustration according to patterns.
    [069] In turn, another advantageous solution provides that the body of the nut is plastically deformed through the action of force on one of the front sides, in particular, the second front side, with a component in the direction parallel to the central axis.
    [070] In cases where on an outer corner of the second front side there is an actuation of force, or on the second front side directly an actuation of force, preferably a thread thread adjacent to the second front side is plastically deformed, deviating from the standard course in order to obtain the necessary tightening torque.
    [071] With respect to the type of action of the deformation forces, so far no more detailed indications have been made.
    [072] Thus, an advantageous solution provides that the body of the nut is plastically deformed through deformation forces that act in the form of a point.
    [073] Alternatively or complement this, another solution provides that the body of the nut is plastically deformed through deformation forces that act linearly.
    [074] Alternatively or complement another appropriate solution provides that the body of the nut is plastically deformed through deformation forces that act in a superficial way.
    [075] With respect to the extent of deformation of the nut body, so far no more detailed indications have been made.
    [076] Thus, an advantageous solution provides that the body of the nut is deformed globally.
    [077] Under the concept deformed globally, in this case, it should be understood that, in total, the nut body, preferably, the polygonal section of the nut body has a shape, which deviates from the standard courses in relation to a shape, in the production according to standard course standards.
    [078] This means that the body of the nut and, in particular, the polygonal section thereof are deformed in total.
    [079] Alternatively or complementary, however, in the same way it is also possible that the body of the nut is deformed, with priority, locally.
    [080] As a priority local deformation, in this case, it should be understood that this deformation acts only locally, therefore, in the area of the sow body, in which this deformation is introduced and, therefore, does not act in such a way that, the body of the nut itself, or the polygonal section thereof, significantly alter its basic shape.
    [081] With respect to the material, from which the nut body was manufactured, in connection with the clarification to date of the solutions according to the invention, no more detailed indications have been made.
    [082] A nut with at least one of the characteristics clarified above may be fabricated from metal, for example, steel, ceramic, glass, polymer, composite material, or a “smart material”.
    [083] In particular, as an alternative or complementary to the characteristics of the execution examples and versions described so far, the task mentioned at the beginning according to the invention is also solved by the fact that the nut body is manufactured steel with a bainitic or ferritic-pearlite structure.
    [084] A steel with a structure of this type allows to give the nuts the most ideal mechanical properties possible, with as little weight as possible and, in particular, a structure of this type allows a particularly profitable manufacture of a nut of this type.
    [085] Thus, an appropriate solution predicts that the bainitic or ferritic-pearlite structure has a carbon content of at least 0.25% by weight or more.
    [086] A carbon content of this type has been shown to be suitable for a nut structure with ideal mechanical properties.
    [087] The strength properties of a bainitic or ferritic-pearlite structure of this type can increase according to the invention, by the fact that the bainitic or ferritic-pearlite structure has increased strength properties through precipitation of microalloy elements.
    [088] In this case, the parts of the microalloy elements are very small.
    [089] Thus, an advantageous solution provides that the bainitic or ferritic-pearlite structure has at least 0.05% by weight of microalloy elements.
    [090] A particularly suitable solution provides that the bainitic or ferritic-pearlite structure has at least 0.1% by weight of microalloy elements.
    [091] In this context, no more detailed indications were made about microalloy elements of this type.
    [092] The elements of microalloys of this type are, for example, Nb, Va, Ti.
    [093] Another advantageous solution provides that the bainitic or ferritic-pearlite structure presents increased strength properties through thermomechanical pretreatment.
    [094] These are thermomechanical pretreatment steps, which are known from the prior art.
    [095] In addition, an advantageous solution provides that the bainitic or ferritic-pearlite structure presents a mixed crystal solidification through, for example, silicon and/or manganese.
    [096] In addition, it is possible to obtain the desired shape strength of the nut body, in particular, in the area of the thread support coating by means of a subsequent heat treatment.
    [097] However, it is particularly advantageous if the desired shape strength of the thread support coating can be achieved by cold transformation of bainitic or ferritic-pearlite structures, and partial production of high displacement densities without subsequent heat treatment, a since this method allows considerable savings in manufacturing costs.
    [098] A proper execution form of a nut provides that the bainitic or ferritic-pearlite structure through the control of the structure conversion and through the transformation presents a hardness in the range of 100 to 370 HV, even better from 110 to 360 HV for normal thread and a hardness in the range of 170 to 370 HV, even better from 180 to 360 HV for fine thread in the thread support coating, without the need for further heat treatment.
    [099] Furthermore, the task mentioned at the beginning is also solved by a method according to one of the claims 48 to 70.
    [0100] Other features and advantages are the object of the description below, as well as the graphical representation of some execution examples.
    [0101] In the drawing it is shown:
    [0102] In fig. 1 is a perspective representation of a first embodiment of a nut according to the invention;
    [0103] In fig. 2 is a top view of the nut in the direction of arrow A in fig. 1;
    [0104] In fig. 3 is a section along line 3-3 in fig. two;
    [0105] In fig. 4, a representation similar to fig. 1 of a second embodiment of a nut according to the invention;
    [0106] In fig. 5, a representation similar to fig. 2 of the second embodiment of the nut according to the invention;
    [0107] In fig. 6, a representation similar to fig. 3 of the second example of embodiment of the nut according to the invention;
    [0108] In fig. 7, a representation similar to fig. 1 of a third embodiment of the nut according to the invention;
    [0109] In fig. 8, a representation similar to fig. 2 of the third example of embodiment of the nut according to the invention;
    [0110] In fig. 9, a representation similar to the
    [0111] In fig. 10, a representation similar to fig. 1 of a fourth embodiment of the nut according to the invention;
    [0112] In fig. 11, a representation similar to fig. 2 of the fourth embodiment of the nut according to the invention;
    [0113] In fig. 12, a representation similar to fig. 3 of the fourth embodiment of the nut according to the invention;
    [0114] In fig. 13, a representation similar to fig. 1 of a fifth embodiment of the nut according to the invention;
    [0115] In fig. 14 is a representation similar to fig. 2 of the fifth embodiment of the nut according to the invention;
    [0116] In fig. 15, a representation similar to fig. 3 of the fifth embodiment of the nut according to the invention;
    [0117] In fig. 16, a representation similar to fig. 1 of a sixth example of embodiment of the nut according to the invention;
    [0118] In fig. 17, a representation similar to fig. 2 of the sixth example of embodiment of the nut according to the invention;
    [0119] In fig. 18, a representation similar to fig. 3 of the sixth example of embodiment of the nut according to the invention;
    [0120] In fig. 19, a representation similar to fig. 1 of a seventh example of embodiment of the nut according to the invention;
    [0121] In fig. 20, a representation similar to fig. 2 of the seventh example of embodiment of the nut according to the invention;
    [0122] In fig. 21, a representation similar to fig. 3 of the seventh example of embodiment of the nut according to the invention;
    [0123] In fig. 22, a representation similar to fig. 1 of an eighth embodiment of the nut according to the invention;
    [0124] In fig. 23, a representation similar to fig. 2 of the eighth embodiment of the nut according to the invention;
    [0125] In fig. 24, a representation similar to fig. 3 of the eighth embodiment of the nut according to the invention;
    [0126] In fig. 25, a representation similar to fig. 11 of the fourth example of embodiment of the nut according to the invention, executed as a first version of a lock nut;
    [0127] In fig. 26, a representation similar to fig. 12 of the first version of a locknut according to the invention;
    [0128] In fig. 27, a representation similar to fig. 25 of a second version of a locknut according to the invention;
    [0129] In fig. 28, a representation similar to fig. 26 of the second version of the locknut according to the invention;
    [0130] In fig. 29, a representation similar to fig. 25 of a third version of a locknut according to the invention;
    [0131] In fig. 30, a representation similar to fig. 26 of the third version of a locknut according to the invention;
    [0132] In fig. 31, a representation similar to fig. 25 of a fourth version of a locknut according to the invention;
    [0133] In fig. 32, a representation similar to fig. 26 of the third version of a locknut according to the invention;
    [0134] In fig. 33, a representation similar to fig. 25 of a fifth version of a locknut according to the invention;
    [0135] In fig. 34, a representation similar to fig. 26 of the fifth version of a locknut according to the invention;
    [0136] In fig. 35, a representation similar to fig. 25 of a sixth version of a locknut according to the invention;
    [0137] In fig. 36, a representation similar to fig. 26 of the sixth version of the locknut according to the invention;
    [0138] In fig. 37, a representation similar to fig. 25 of a seventh version of the locknut according to the invention and
    [0139] In fig. 38, a representation similar to fig. 26 of the seventh version of the locknut according to the invention;
    [0140] In fig. 39, a steel composition with a ferritic-pearlitic precipitation hardening structure according to the invention and
    [0141] In fig. 40, a composition of properties and compositions of a steel from a precipitation hardening ferritic-pearlite structure according to the invention with good cold-forming properties.
    [0142] A first example of execution shown in figures 1 to 3 of a nut according to the invention, designated as a whole with 10 comprises a nut body 12, which extends along a central axis 14, between a first front side 16 and a second front side 18.
    [0143] The nut body 12 is traversed by a threaded hole 20, which extends parallel to the central axis 14 from the first front side 16 to the second front side 18, which has an internal thread 22 with threads 24, which extend from a predetermined central hole diameter DK by an inner contour of the thread threads 24, to a nominal diameter or outer diameter DA predetermined by an outer contour of the thread threads 24, into the body of the nut 12, and which are supported by a thread-support liner 30 that surrounds the threads of the thread 24, which is part of the body of the nut 12.
    [0144] The cylindrical thread support coating 30, which represents an integral component of the body of the nut 12, gives the threads 24 the necessary stability against their deviation in the radial direction and/or in the axial direction with respect to the axis central 14, by means of its wall 34 closed in a direction of the circumference 32 circulating around the central axis 14, the wall 34 of the thread support coating 30, starting from the outer diameter DA in the radial direction with respect to the axis center 14 has a thickness DG, corresponding to at least 0.05 times the external diameter DA of the internal thread 22, in order to stabilize the threads of the thread 24, in the case of a load through a threaded pin 36 screwed with a external thread 35 corresponding to the threads of the thread 24, against a movement in the radial and/or axial direction with respect to the central axis 14.
    [0145] The nut body 12 is provided with a polygonal outer contour 40, in a polygonal section 38, which in the first example of execution extends from the first front side 16 to the second front side 18, whose contour is defined by the areas corners 42 and key surfaces 44 which lie between corner areas 42, wherein key surfaces 44 which are opposite each other with respect to the central axis 14 pass parallel to each other, and pass at an interval, which is defined by a common standard for nuts 10, eg DIN EN 1661, 1663, 1664, 1667, DIN EN ISO 4032 - 4036, DIN EN ISO 8673 - 8675, DIN EN ISO 7040 - 7042, DIN EN ISO 7719, DIN EN ISO 10511 - 10513, as well as DIN EN ISO 4759 - 1, such that the outer contour 40 respectively has an even number of key surfaces 44, which run parallel to each other in pairs. corner areas 42 represent, respectively, a passage between successive key surfaces 44 in the direction of the circumference 32.
    [0146] In the case of the nut 10 shown, the polygonal outer contour 40 is executed as a hexagonal shape with a regular hexagon cross-sectional shape in accordance with the “Tabellenbuch Metall/Metal table book”, 44a. Edition, Verlag Europa Lehrmittel, page 59, such that six corner areas 42 and six key surfaces 44 are located, respectively, between successive corner areas 42 in the planes of key surfaces 46, the planes of key surfaces 46 respectively pass parallel to central axis 14 and are aligned such that planes of key surfaces 46 which are respectively opposite to each other pass parallel to central axis 14 which lie between these planes, and parallel to each other.
    [0147] According to the first example of embodiment, in the case of the nut body 12 according to the invention, the key surfaces 44 extend in a transverse direction 48 which lies in the respective plane of key surfaces 46, between the successive corner areas 42 not interconnecting and closed at key surface planes 46, but key surfaces 44 are formed by key surface areas 52 and 54, which lie in key surface planes 46, preferably , the key surface areas 52 and 54 respectively extend, after one of the corner areas 42, towards the other respective corner area 42, however, they do not pass one inside the other.
    [0148] On the contrary, between the key surface areas 52 and 54 is situated a recess 60, extending in the direction of the central axis 14, starting from the respective key surface plane 46 into the nut body 12, which adjacent to the key surface areas 52 and 54 has sidewall areas 62 and 64 passing transverse to these areas, as well as a bottom area 66 connecting the sidewall areas 62 and 64, which is made concave convex. , and protrudes so far into the nut body 12 that this body touches the thread support liner 30.
    [0149] Preferably, the bottom area 66, in this case, is concave domed, such that it passes through the side wall areas 62 and 64, likewise concave domes, such that, in a plane of cross section QE corresponding to the intermediate plane in fig. 2, which runs perpendicular to the central axis 14, the recess 60 has a U-shaped cross-sectional shape, preferably even a cross-sectional shape extending approximately a circular segment.
    [0150] In the nut body 12 according to the invention, the corner areas 42, the key surface areas 52 and 54, as well as the side wall areas 62 and 64 and in part the bottom area 66 are supported by outer contour brackets 70 of the nut body 12, which likewise represent an integral component of the nut body 12, and therefore are also molded in one piece on the thread support liner 30, and starting from the thread support liner 30 respectively extend radially outwardly with respect to the central axis 14, and which in this case support the surfaces mentioned above.
    [0151] Starting from the corner areas 42, the key surface areas 52 and 54 that form the key surfaces 44 in the respective plane of the cross section QE that pass perpendicular to the central axis 14, for example, to the drawing plane in fig. . 2, through a width B52 and a width B54 in a transverse direction 48, which together with at least 10% of a gap AK matter in adjacent corner areas 42, such that, conversely, the recess 60 has a width BA in the plane of the QE cross section which passes perpendicular to the central axis 14, which has at most 90% of the AK interval of the successive corner areas 42.
    [0152] The outer contour 40 defined only through the key surface areas 52 and 54, as well as the corner areas 42, and executed according to the pattern in these areas, in the first execution example, in the polygonal section area 38 of the nut body 12 is identical in each plane of the cross-section QE that passes perpendicular to the central axis 14, such that in the polygonal section 38 they can grip usual tools provided for such a polygon according to the pattern, with the respective SW wrench width in order to be able to screw and unscrew nut 10 with internal thread 22 on a threaded stud.
    [0153] In the example of execution shown in fig. 1 of a nut 10 according to the invention, the nut body 12 does not extend beyond the polygonal section 38, i.e. the nut body 12 is formed only by the polygonal section 38, such that, for example, the front side 16 represents a pressing surface 82, with which an element to be screwed or a body to be screwed can be admitted.
    [0154] In addition, the cross-sectional shape of the nut body 12 in the entire polygonal section 38 is identical in each plane of the cross-section QE that passes perpendicular to the central axis 14, such that along the entire length of the nut body, between the first front side 16 and the second front side 18 this section has the identical cross-sectional shape.
    [0155] Thus, in the first example of execution, in total the body of the nut 12 is executed in such a way that, except for the course of the internal thread 22, this body presents a rotation symmetry of six digits around the central axis 14 .
    [0156] If, in this case, on the pressure side 82 an element is admitted with a pressure surface 84, then, on the thread support coating 30 there are forces acting close to the pressure side 82 in the direction of the circumference 32, the which act towards a maximum widening of the thread support coating 30, and decrease with increasing interval on the pressure side 82, such that the thread support coating 30 in total must be dimensioned in such a way that, the radial thickness DG of its wall 34 is sufficient to absorb the collective load of forces and moments, which acts in the case of the anticipated load of the nut body 12, then to the pressure side 82 (fig. 3).
    [0157] In a second example of execution, shown in figures 4 to 6, the polygonal section 38 likewise extends through the entire body of the nut 12', from the first front side 16 to the second front side 18, along the central axis 14, however, the recess 60' does not extend from the second front side 18 to the first front side 16, but to a pressure bottom 90 representing an integral component of the nut body 12', in the area of the pressing side 82', which extends between the corner areas 42 radially following the central axis 14, to the planes of key surfaces 46, such that, in the area of the pressing bottom 90, forms an area of key surfaces 56, which extends in the transverse direction 48 continuously between the corner areas 42.
    [0158] In the second example embodiment, the recess 60' passes through the second front side 18 towards the first front side 16, therefore only up to the pressure bottom 90 and therefore through a partial section TA of the extension of the nut body 12' in the direction of the central axis 14, and ends with a closure wall 92, which is aligned parallel to a cross-sectional plane QE, which passes perpendicular to the central axis 14, and represents an upper side of the bottom of pressure 90, which is opposite a pressure surface 84'.
    [0159] Due to the fact that, in the second example of execution, the pressure bottom 90 extends well radially outwards in the area of the pressure side 82', in the area of the first front side 16, the radial thickness DG 1 of the coating of thread support 30 is greater than in the area of the second front side, in which the radial thickness DG 2 of the thread support coating 30 is limited by the bottom area 66' of the recess 60'.
    [0160] Thus, in the area of the pressure side 82', the thread support coating 30' has a greater radial thickness DG1, and therefore, in the area of the pressure side 82', it gives the internal thread 22 a stability greater against a radial and/or axial widening of the same.
    [0161] Through the pressure bottom 90, therefore, in the area of the pressure side 82', a further reinforcement of the thread support coating 30 takes place against a widening in the direction of the circumference 32.
    [0162] In addition, through the pressure bottom 90 there is also a reinforcement of the external contour supports 70, one in relation to the other, in such a way that in this way the whole body of the nut 121 is in the situation to absorb greater loads.
    [0163] In a third example of embodiment, shown in figures 7 to 9, likewise, those parts which are identical to those of the first example of embodiment are provided with the same reference numerals, so that reference can be made integrally to the executions of the previous execution examples.
    [0164] In contrast to the second example of embodiment, in the third example of embodiment, in the pressure bottom area 90, a pressure flange 100 is provided radially above the polygonal body 38, which in relation to the central axis 14 it has an outer contour 102 circular, such that in the area of the pressure side 82" of the nut body there is an enlarged pressure surface 84" which raises a cross-sectional surface of the polygonal section 38, which projects radially therein. example of execution in addition to the pressure flange 100 in the direction parallel to the central axis 14. The polygonal section 38 is executed in the same way as in the second example of execution, since, in the same way as in the second example of execution, starting from the second front side 18, towards the first front side 16", the recess 60' extends only to the pressure bottom 90 and ends in the area of the pressure bottom 90, with the closing wall 92.
    [0165] In this case, as described in the second example of execution, in the same way, the closing wall 92 passes parallel to the cross-sectional planes QE, which pass perpendicular to the central axis 14.
    [0166] In a fourth example of execution, shown in figures 10, 11 and 12, as the same reference numbers are used, the body of the 12"' nut is executed in the same way as in the previous examples of execution, in such a way that, for this, it can be sent in full to executions.
    [0167] In particular, the 12" nut body comprises the polygonal section 38, with the pressure bottom 90 and the pressure flange 100 according to the third example of execution.
    [0168] As opposed to the third example of execution, however, the closing wall 92"' of the 60"' recess does not pass parallel to a plane of cross section QE, but at an angle α in relation to this plane and therefore , starting from the bottom area 66"' of the recess 60"' is slanted outward with increasing radial extension with respect to the central axis 14, such that the closing wall 92"' falls radially outwards towards the pressure flange 100.
    [0169] In a fifth embodiment shown in figures 13 to 15, likewise, those parts, which are identical with those of the previous embodiment examples, are provided with the same reference numerals, such that, with respect the description of the same ones can be made full reference to the executions of the previous execution examples.
    [0170] As opposed to the previous execution examples, in the fifth execution example the bottom area 66"" of the 60"" recesses are executed in such a way that, in the area of the second front side 18, this area has a maximum depth, this is, a maximum range of the plane of keys surfaces 46, which decreases increasing, with increasing extension of the bottom area 66"" towards the first front side 16, this means that, in total the bottom area 66"" passes at an acute angle to the central axis 14, and on reaching the pressure bottom 90 it also reaches the plane of keys surfaces 46.
    [0171] An extension of the 60"" recess from the second front side 18 towards the first front side 16, in this case, is limited, for example, to a partial section TA of the 12"" nut body, whose length matters in less than half the length of the 12” nut body, from the first front side 16 to the second front side 18.
    [0172] In this example of execution, therefore, in the same way, the radial thickness DG of the 34"" wall of the 30"" thread support coating is already in approximately half of the extension of the body of the nut 12 from the second front side 18 for the first front side 16 is significantly larger than in the area of the second front side 18 and continues to the radial thickness DG 1 in the area of the first front side 16 and the pressure flange 100 existing in that area.
    [0173] In a sixth example of execution, represented in figures 16 to 18, as opposed to the fifth example of execution, the bottom area 66""' of cavity 60""' is not executed straight, but passes from the second front side 18 towards the first front side 16 in a concave domed shape, until reaching the respective plane of key surfaces 46.
    [0174] Otherwise, the sixth running example is performed in the same way as the fifth running example, such that, with respect to other details, full reference can be made to the runs in relation to the fifth running example, and also to the previous execution examples.
    [0175] In a seventh example of execution, shown in figures 19 to 21, the 60""" recesses are executed in such a way that they do not have any cross section approximately U-shaped, as in the context with the examples of execution described so far, but an approximately rectangular cross-section, with the side wall areas 62""" and 64""" extending, first almost perpendicularly to the plane of keys surfaces 46 into the body of the nut 12""", and then pass with insignificant rounding to the bottom area 66""", which with the exception of the rounded passages in relation to the 62""" and 64""" sidewall areas passes approximately parallel to the plane of switch surfaces 46, between the side wall areas 62""" and 64""" and, above all, starting from the second front side 18 with increasing extension in the direction parallel to the central axis 14, passes outwards with reference to the central axis 14 and consequently drops rad outwardly towards the pressure flange 100.
    [0176] Therefore, starting from the second front side 18 of the nut body, the bottom area 66""" passes towards the first front side 16 at an acute angle α""" with respect to the central axis 14, falling radially outwards towards the first front side 16 and thereby after extension through the partial section TA reaches the plane of switch surfaces 46.
    [0177] Moreover, in the seventh embodiment, the other elements of the nut 10 according to the invention, insofar as these elements are identical with the preceding embodiments, are provided with the same reference numerals, in such a way that, full reference can be made to the executions of the previous execution examples.
    [0178] In an eighth example of execution, shown in figures 22 to 24, the cavity 60"""' is irregularly shaped, in such a way that, for example, the bottom area 66"""' is irregularly undulated partially , both in the direction of its extension from the second front side 18 towards the first front side 16 of the nut body 12"""' and also in the transverse direction 48 between the corner areas 42, such that both the totality of the sidewall areas 62"""' and 64"""" in connection with the background area 66"""' can have any irregular shape, the maximum range of the background area 66"""' of the respective plane of keys surfaces 46 fix the radial thickness DG of the wall 34 of the 30”””' thread support coating.
    [0179] In this case, the recesses 60"""' of the second front side 18 may extend towards the first front side 16 to the pressure flange 100, eventually, however, they may also present only along an extension through a partial section TA, such that, between the respective recess 60”””' and the pressure flange 100, there is still the formation of a pressure bottom 90.
    [0180] In the context of all the preceding examples of execution, there is the possibility of executing the nut according to the invention as a conventional nut, that is, as a nut, whose internal thread 22 can be easily screwed onto the threaded pin 36 and, in In particular, it does not have any tightening torque when screwing or unscrewing and therefore has no insurance against loss.
    [0181] As an alternative, however, it is also possible to execute the nuts 10 and, in particular, the nuts 10 according to all the implementation examples described above, as locknuts 10S, that is, to execute these nuts in such a way that , during the screwing of the internal thread 22 on the threaded pin 36, a tightening torque occurs, which prevents the nut from being automatically released from the state when screwed, due to a dominant load collective. tightening torque should be specifiable, preferably, depending on the purpose of application.
    [0182] With the aid of the fourth embodiment shown above, several alternative or additional possibilities of the invention are shown below, as a defined tightening torque of polygonal nuts in general, in particular, can be specified in a simple way. , also of polygonal nuts executed according to the first to the eighth execution example.
    [0183] In the case of a first version in figures 25 and 26 of a 10S nut according to the invention, whose nut body 12 has a polygonal section 38, a deformation of the polygonal section 38 occurs due to the action of a point deformation force DKP, for example, in corner sections 42 that are opposite each other, for example, in only two corner sections 42 that are opposite each other of outer contour supports 70 that are opposite each other, such that , upon deformation of the polygonal section 38, a plastic deformation of the internal thread 22 occurs, such that, for example, in the area of the external contour supports 70 admitted by the deformation forces acting in a point shape, the GBD thread areas that are opposite each other in relation to the central axis, have a smaller AGD gap between them than the GB thread areas that lie outside the GBD thread areas, such that, when screwing these 10S nuts according to the firstversion, the GBD deformed thread areas, whose AGD interval is smaller than specified by the standard, when screwing the threaded pin 36 with the external thread 35 into the internal thread 22, by means of elastoplastic deformation of the polygonal section 38 to the internal thread 22 is enlarged again for the measurement of the screwed threaded stud 36, in such a way that the polygonal section 38, which presents an overall elastoplastic shape resistance, undergoes a preponderance of an elastoplastic shape change as a whole, and therefore produces a reaction force this, with which the GBD deformed thread areas press on the external thread 35 of the threaded pin 36 to be screwed in and thereby produce the desired tightening torque.
    [0184] Since, in this example of execution, the plastic deformation of the polygonal section 38, produced by the point deformation forces DKP predominantly represents a global deformation of the polygonal section 38, the forces produced by the change in elastoplastic shape, with which the sections of the GBD deformed thread act on the external thread 35 of the screwed threaded pin 36, likewise, are defined with preponderance through the resistance to the global elastoplastic shape of the polygonal section 38.
    [0185] The action of the DKP point deformation forces on the corner sections 42 preferably occurs in an upper area 112 of the corner areas 42, which are close to the second front side 18, since in this upper area 112 the polygonal section 38 has a plastic deformation capacity greater than in the area of pressure bottom 90 or pressure flange 100, such that the path that external thread 68 of threaded pin 36 travels through the deformed area with minimum gap AGD is minor.
    [0186] Preferably, the upper area 112 extends, in this case, starting from the second front side 18 up to a maximum of half the extension of the recess 60"' from the second front side 18 towards the first front side 16 or the pressing side 82, preferably up to one third of the extent of the recess 60"', from the second front side 18 towards the first front side 16.
    [0187] In the first version of the locknut 10S according to the invention, the punctual deformation forces DKP are aligned in such a way that they act radially and transversely to the central axis 14, preferably perpendicularly to that axis.
    [0188] But there is also the possibility of letting the deformation forces acting in the form of a DKP point act either with a component towards the first end side 16, or both with a component towards the second end side 18.
    [0189] The forces acting in the form of a DKP point leave 12 pressure points 114 in the form of a point on the nut body, in which its action is recognizable.
    [0190] In a second version of a 10S locknut made according to the invention, shown in figures 27 and 28, the action of deformation forces not in the form of deformation forces that act in the form of a DKP point occurs, but in the form of deformation forces acting linearly DKL on the corner areas 42 in the upper area 112, which likewise lead to deformations of the polygonal section 38 similar to those of the type described in context with the first version, being that, with the linearly acting deformation forces DKL, likewise, there is, in essence, a deformation of the polygonal section 38 as a whole.
    [0191] Similarly, as in the first version, the deformation forces that act linearly DKL can be two deformation forces that act relative to each other DKL in pairs relative to the central axis 14, or several deformation forces DKL acting, preferably, respectively, at regular angle intervals in relation to the central axis 14, with similar deformations approximately of the polygonal section 38 as in the first version and, where, the DKL deformation forces leave pressure points 116 linearly on the body of the nut 12.
    [0192] Also in the case of using linearly acting deformation forces DKL, according to the second version, linearly acting deformation forces DKL are directed in such a way that they pass transversely to the central axis 14, for example, perpendicular to that axis.
    [0193] But there is also the possibility to let the deformation forces that act linearly DKL or both act with one component towards the first end side 16, or both with one component towards the second end side 18.
    [0194] In a third version of a locknut according to the invention, shown in figures 29 and 30, in the same way, a nut body 12 is used according to the fourth example of execution, and an actuation occurs in this case, not in the area of the external contour supports 70, but in the area of the bottom 66"', and in the third version, likewise, deformation forces are used that act in the form of a DKP point in the upper area 112, which with preponderance lead to a deformation of partial areas of the thread support coating 30, adjacent to the point-shaped pressure points 114 and, therefore, produce deformed GBD thread areas", whereby the deformation is located stronger, since also already the thread support coating 30 in opposition to the outer contour supports 70 by virtue of a minimum thickness undergoes a primary local elastoplastic deformation, which likewise results in a local elastoplastic deformation of the internal thread 22 and thereby leads to a deformed GBD thread area”.
    [0195] During the screwing of a 10S" lock nut of this type, according to the third version, in the external thread 35 of a threaded pin 36, the force produced by the elastoplastic deformation is generated, which acts on the deformed thread areas GBD" in that primarily the local plastic deformation of the thread support liner 30 is regressed, through the return of the local elastoplastic deformation of the thread support liner 30 during screwing of the threaded stud 36, at least partially.
    [0196] In this case, however, the return of the local elastoplastic deformation can also still additionally overlap, with a total deformation of the polygonal section 38, which allows moving the GBD deformed thread areas from each other again in such a way that , the threaded pin 36 can be screwed into the internal thread 22, meanwhile generating the desired tightening torque.
    [0197] The locally produced deformation with preponderance through acting on the bottom area 66"' of the 60"' recess, but can also be additionally combined with a preponderantly global deformation of the polygonal section 38 through the complementary action of forces of DKP or DKL deformation on corner areas 42, as in context with the first or second version.
    [0198] The deformation forces acting in the form of a DKP point according to the third version are preferably likewise oriented transversely to the central axis 14, in particular perpendicular to that axis.
    [0199] But there is also the possibility of giving these deformation forces that act in the form of a DKP point a component in the direction of the first front side 16 or the second front side 18.
    [0200] In a fourth version of a 10S”’ locknut according to the invention, shown in fig. 31 and in fig. 32, in the bottom area 66 there is no point-shaped actuation, but linearly acting deformation forces DKL are used, which in this version, for example, are effective in all bottom areas 66 of the polygonal section 38 , in order to produce, corresponding to the number of the bottom areas 66, several times around the central axis 14, for example, the deformed thread areas GBD"'1 to GBD"'6 the forces that arise predominantly through local deformation of the thread support coating 30, such that these six deformed thread areas GBD"'1 through GBD"'6 arranged around the central axis 14 are responsible for the tightening torque of the internal thread 22, generated during the screwing them onto a threaded pin 36.
    [0201] The linearly acting deformation forces DKL provided for in the fourth version, for example, pass transversely to the central axis 14, preferably perpendicular to that axis or also with a component in the direction of the first front side 16, or from the second front side 18 and leave the pressure points 116 linearly.
    [0202] In principle, the value and direction of the linearly deformed thread areas GBD”’1 to GBD”’6 in pairs can be different.
    [0203] As in the case of a fifth version of a 10S"" locknut according to the invention, shown in figures 33 and 34, as an alternative to the forces acting in the form of a DKP point or to the forces that act in a linear manner DKL can also be used surface-acting forces DKF, which in the fifth version act superficially in the bottom area 66"' of the 60"' recesses with the production of pressure points 118 superficially and thus correspondingly when acting superficially, they produce an elastoplastic deformation as always, with local preponderance, however, distributed over a larger surface area of the thread support coating 30 and, with this, produce deformed GBD"" thread areas performed on a large scale.
    [0204] Also DKF surface-acting deformation forces of this type on the 66"' bottom areas can be effective or on a pair of 66"' bottom areas that are opposite each other, or on three individual or several 66"' bottom areas that are opposite each other in pairs, or can also be combined with deformation forces acting on corner areas 42, whether they are point deformation forces DKP or linear form deformation forces DKL, or also eventually DKF surface shape deformation forces.
    [0205] In the case of the fifth version, the surface-acting deformation forces DKF are primarily aligned in such a way that they act transversely to the central axis 14, whereas the surface-acting deformation forces DKF , but also the two that can have, respectively, a component towards the first front side 16, or towards the second front side 18, in order to be able to produce, in the area of a partial surface of their action, even a reinforced plastic deformation , in particular, a plastic deformation with local preponderance in the thread support body 30 and, therefore, also in the area of the corresponding GBD"" deformed thread of the internal thread 22.
    [0206] In a sixth version of a 10S""" locknut according to the invention, shown in figures 35 and 36, an actuation occurs on the corner areas 42 not in the upper area 112, but, for example, through linearly acting deformation forces DKL, on an upper outer corner 122 adjacent to the second front side 18 and, for example, two corner areas 42 which are opposite each other, or several corner areas 42 which are opposite each other. the other, respectively, in pairs, in such a way that the deformation forces DKL act on the external contour supports 70 respectively, and thus lead to a preponderantly global deformation of the polygonal section 38 in direct connection with the second front side 18, such that, in particular, deformed thread areas GBD””' appear in the area of the threads of the internal thread 32, which connect directly to the second end face 18.
    [0207] In this case, the deformation forces that act linearly DKL are preferably oriented such that, on the one hand, they act in the direction of the central axis 14, and on the other hand, in the direction of the front side 16 .
    [0208] Also in this example of execution, only two deformation forces DKL that are opposite to each other in relation to the central axis 14 can act, or also several deformation forces DKL that are opposite to each other, respectively, in pairs.
    [0209] In the case of a seventh version of a 10S""" locknut according to the invention, shown in Figures 37 and 38, axial deformation forces DKAL act linearly aligned parallel to the central axis 14 and actually aligned radially to the central axis 14, on the second front side 18 in the area of the thread support coating 30 by producing pressure points 120 in a linear fashion, and lead to a plastic deformation surrounding around the central axis 14, of the first thread of the thread 24 adjacent to the second front side 18 of the internal thread 22, which thus undergoes, for example, in total one closely with respect to its diameter from the central hole DK, and in the direction of the central axis 14 with reference to a standard course presents deformed thread areas, whose interval is reduced in relation to the standard pitch. This deformation, which during screwing of the threaded pin 36 into the internal thread 22 leads, in total, to an elastoplastic widening of the polygonal section 38, in particular, close to the second front side 18, and this elastoplastic widening, in turn, leads reaction forces that press one of the first threads against the external thread 35 of the screwed threaded stud 36, which therefore is responsible for the desired tightening torque.
    [0210] In general, in the first to the seventh version according to the invention there is the possibility of combining together the plastic deformations that can be produced by the deformation forces DK, which have consequences on the range of areas of the shaft thread center 18 and over the course of the threads in relation to each other, in order to thereby, for example, also obtain, through multiple deformations of the polygonal section 38, the desired tightening torque during screwing and unscrewing of the internal thread on a threaded stud.
    [0211] A nut 10 according to the invention can preferably be manufactured from a material with a bainitic or ferritic-pearlite basic structure according to annex 1. In both types of material, through a specific control of the transformation of the structure an advantageous combination of tensile strength and deformation capacity is obtained.
    [0212] Through additions of microalloy elements and thermomechanical pretreatment processes, properties are generated before the molding process itself, which as a result of the molding itself (cooling of forging heat in hot molding processes or increased precipitation in cold molding processes) lead to mechanical properties of defined structure, which would need to be adjusted, for example, using conventional cold compression loads, through a separate hot treatment process, after the molding process itself.
    [0213] Starting from a material with a bainitic or ferritic-pearlite basic structure of this type occurs, for example, a cold molding or a cold pressure extrusion of a starting material, for example, of a wire or a material from a bar in at least one molding stage or in several molding stages to a shape of the nut body 12 according to one of the embodiment examples described above, and/or one of the versions described above.
    [0214] During this process of molding the material mentioned above, due to the formation of precipitation and/or increased precipitation density, there is a solidification of the material due to the heterogeneous formation of the cross section in different intensity, and, in particular, in the area with thinner cross section a stronger deformation arises than in areas with correspondingly thicker cross section.
    [0215] In particular, molding leads to an increase in strength around at least 5% compared to the starting material, even better, around at least 10% or even better at least 20% starting from starting material strength values.
    [0216] For example, a stronger solidification of the thread support coating 30 of the nut body 12 occurs in the area of the recesses 60, which contributes to an improved stabilization of the internal thread 22 against load deformation through the threaded stud 36. In this case, as a result of the displacement density gradient produced through the molding, starting from the key surfaces 44 increasing relative to the thread support coating 30, a possible heat treatment following the molding process can be waived. since in the area of higher structural mechanical requirements, as in the thread support coating 30, by combining higher precipitation densities and material with bainitic or ferritic-pearlite basic structure a sufficient hardness can be obtained.
    [0217] For example, the hardness of the thread support coating 30 for fine thread is in the range of 180 to 360 HV, for normal thread, in the range of 110 to 360 HV.
    [0218] As an example for a precipitation hardening ferritic-pearlite material, or precipitation hardening ferritic-pearlite steel is referred, for example, to the material 24MnSiV5, or to the material 27MnSiV6, and the material mentioned last has the properties listed in annex 2, as well as the chemical composition mentioned in annex 2.
    [0219] In this case, strength is obtained through mixed crystal solidification with Si, Mn and/or precipitation hardening with Va, Nb, Ti.
    权利要求:
    Claims (16)
    [0001]
    1. NUT, comprising a nut body (12) provided or may be provided with an internal thread (22) which has a polygonal section (38) with an external polygonal contour (40) which, on the one hand, has corner areas (42) and, on the other hand, has key surfaces (44) which lie between corner areas (42) which extend in planes of key surfaces (46) that pass according to patterns, whereby, the nut body (12) has several recesses (60) which, starting from the respective key surface planes (46) extend into the nut body (12), in the direction of the hole (20), in which the nut body (12) has a first front side (16) made with a pressure surface (84) as the depression side (82), and a second front side (18), remote from the pressure side (82) in which the recess (60) extends from the respective plane of keys surfaces (46) to a thread support liner (30) which surrounds stabilizing the thread. internal (22), wherein the recess (60) extends to the second front side (18), wherein the recess (60) extends to a pressure flange (100) provided on the pressure side (82) at that the minimum thickness (DG) of the thread support coating (30) is greater in the area of the pressure side (16) than in the area of the second front side (18), characterized by, starting from an outer diameter (DA) of the internal thread (22), the thread supporting coating (30) has a minimum radial thickness (DG), which amounts to 0.05 times the external diameter (DA) of the internal thread (22).
    [0002]
    NUT according to claim 1, characterized in that the thread supporting coating (30) has a radially increasing minimum thickness (DG) with increasing extension from the second front side (18) to the pressure side (16).
    [0003]
    3. NUT according to any one of claims 1 to 2, characterized in that in each cross-sectional plane (QE) that passes perpendicularly to a central axis (14) of the internal thread (22) through the polygonal section (38) the sum of the dilation of the areas of key surfaces (52, 54) in a transverse direction (48) between, respectively, two successive corner areas (42) matters at least in 10% of an interval (AK) of these areas corner (42) in the transverse direction (48).
    [0004]
    4. NUT according to any one of claims 1 to 3, characterized in that the recesses (60) present in a cross-sectional plane (QE) which respectively passes perpendicular to a central axis (14) of the internal thread (22) through of the polygonal section (38) the same shape as the cross section.
    [0005]
    5. NUT according to any one of claims 1 to 4, characterized in that the recesses (60) have a cross-sectional shape, which is determined by a bottom area (66) and connects to the side wall areas (62, 64), which pass transversely to the respective plane of key surfaces (46) adjacent to the bottom area (66).
    [0006]
    6. NUT according to any one of claims 1 to 5, characterized in that the recess (60) has a constant or variable cross-sectional shape with an extension in a direction parallel to the central axis (14).
    [0007]
    A NUT according to any one of claims 1 to 6, characterized in that the bottom area (66) has a variable range of the central axis (14) along its length in the direction of the central axis (14).
    [0008]
    8. NUT according to any one of claims 1 to 7, characterized in that the internal thread (22) is manufactured for forming the nut as a lock nut (105), as an internal thread corresponding to standard dimensions, however, through deformation plastic of the nut body (12) is performed deviating from a standard course.
    [0009]
    9. NUT according to claim 8, characterized in that, due to the plastic deformation of the nut body (12), the internal thread (22) has radial intervals (AGD) variable from the central axis (14), which deviate from a standard course, and/or thread fillet gap courses, which deviate from a standard course.
    [0010]
    10. NUT according to any one of claims 1 to 9, characterized in that the nut body (12) is made of steel with a bainitic or ferritic-pearlite structure.
    [0011]
    11. NUT according to claim 10, characterized in that the bainitic or ferritic-pearlite structure has a carbon content of at least 0.25% by weight or more.
    [0012]
    12. NUT according to any one of claims 10 or 11, characterized in that the bainitic or ferritic-pearlite structure presents increased strength properties through precipitation of microalloy elements.
    [0013]
    13. NUT according to claim 12, characterized in that the bainitic or ferritic-pearlite structure has at least 0.05% by weight of microalloy elements.
    [0014]
    14. NUT, according to any one of claims 10 to 13, characterized in that the bainitic or ferritic-pearlite structure presents increased strength properties through thermomechanical pretreatment.
    [0015]
    15. NUT according to any one of claims 10 to 14, characterized in that the bainitic or ferritic-pearlite structure presents a mixed crystal solidification through silicon and/or manganese.
    [0016]
    16. NUT according to any one of claims 10 to 15, characterized in that the bainitic or ferritic-pearlitic structure has a hardness in the range of 100 to 370 HV, even better from 110 to 360 HV for normal thread due to the control of the wall of the structure and due to transformation, and a hardness in the range of 170 to 370 HV, even better of 180 to 360 HV for fine thread in the thread support coating (30) without further heat treatment.
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    同族专利:
    公开号 | 公开日
    US11193524B2|2021-12-07|
    DE102012100850A1|2013-08-01|
    CN104136788A|2014-11-05|
    EP2809958A2|2014-12-10|
    WO2013113871A3|2013-10-24|
    JP2015508870A|2015-03-23|
    KR102138754B1|2020-07-29|
    KR20130089194A|2013-08-09|
    CN104136788B|2018-01-05|
    WO2013113871A2|2013-08-08|
    US20170159696A1|2017-06-08|
    MX2014009237A|2015-05-15|
    JP6280053B2|2018-02-14|
    US20130195581A1|2013-08-01|
    BR112014018857A2|2017-06-20|
    US9624962B2|2017-04-18|
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    法律状态:
    2018-12-04| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-10-22| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-11-10| B07A| Application suspended after technical examination (opinion) [chapter 7.1 patent gazette]|
    2021-07-20| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-08-24| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 01/02/2013, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102012100850A|DE102012100850A1|2012-02-01|2012-02-01|mother|
    DE102012100850.7|2012-02-01|
    PCT/EP2013/052029|WO2013113871A2|2012-02-01|2013-02-01|Nut|
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